EP1601869B1 - Soupape comportant un element ressort pour un injecteur de carburant - Google Patents

Soupape comportant un element ressort pour un injecteur de carburant Download PDF

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Publication number
EP1601869B1
EP1601869B1 EP04737280A EP04737280A EP1601869B1 EP 1601869 B1 EP1601869 B1 EP 1601869B1 EP 04737280 A EP04737280 A EP 04737280A EP 04737280 A EP04737280 A EP 04737280A EP 1601869 B1 EP1601869 B1 EP 1601869B1
Authority
EP
European Patent Office
Prior art keywords
valve
spring element
valve body
bore
valve according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04737280A
Other languages
German (de)
English (en)
Other versions
EP1601869A1 (fr
Inventor
Jürgen Dick
Heinz Lixl
Johann Massinger
Martin Simmet
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Automotive GmbH
Original Assignee
Siemens VDO Automotive AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens VDO Automotive AG filed Critical Siemens VDO Automotive AG
Publication of EP1601869A1 publication Critical patent/EP1601869A1/fr
Application granted granted Critical
Publication of EP1601869B1 publication Critical patent/EP1601869B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps

Definitions

  • the invention is directed to a valve of a fuel injector having a valve housing with a sealing seat for a valve body, with a spring element which biases the valve body in a closed position on the sealing seat.
  • a control valve for a fuel injection valve which comprises two spherical valve members with two valve seats.
  • a diaphragm spring biases the control valve against a sealing surface of the control valve seat.
  • Out DE 199 58 239 goes out an injector with a valve that limits a flow from a control room.
  • fuel is passed with a very high pressure from a high pressure accumulator via a high pressure bore via an inlet throttle to a control room.
  • the fuel pressure acts on a rear end of an axially movable nozzle needle.
  • the movement of the nozzle needle opens and closes injection holes leading to the combustion chamber of an internal combustion engine.
  • the injection holes are at ge opened injection valve with a nozzle chamber in communication formed at the front end of the nozzle needle and which in turn is connected to the high-pressure accumulator.
  • the nozzle needle If the full fuel pressure is present at the nozzle needle both in the control chamber and in the nozzle chamber, the nozzle needle is pressed down due to the larger effective area in the control chamber and closes the injection holes. If the valve is closed, essentially the full fuel pressure is present in the control chamber, so that the nozzle needle closes the injection holes which lead into the combustion chamber of the internal combustion engine.
  • valve When the valve is opened, the fuel pressure acting on the nozzle needle from the control chamber decreases, while the pressure in the nozzle chamber remains the same, so that the nozzle needle of a Seals seat lifts and fuel is injected from the nozzle chamber via the injection holes in the combustion chamber of the internal combustion engine.
  • the valve has a closing member which is biased by a spring against a sealing seat. The spring is in the control room, ie arranged on the high pressure side.
  • the object of the invention is to provide a simplified structural design of such a valve in order to thereby simplify the handling during assembly while reducing the size of the valve.
  • the downstream side of the valve is far more accessible for the assembly of the valve body acting spring element as the high pressure side and therefore offers favorable conditions for a rational assembly.
  • the design of the valve can be simplified as well as downsize. Due to the direct approach of the spring element on the valve plate, an improved reaction speed of the valve is achieved. Likewise, the spring element can be installed in the relaxed state and adapted to the spatial conditions.
  • the spring element between the valve housing and the valve cone is clamped.
  • this side of the valve is easily accessible, which in turn favors the assembly. Due to a smaller number of items, the valve according to the invention is cheaper to manufacture. In addition, this also allows a faster response of the valve, since no further lifting or pushing element is required, as in the prior art.
  • valve body may be provided with a groove whose inner diameter is smaller and whose outer diameter is greater than the diameter of the bore of the spring element engaging in the groove.
  • This generally circumferential groove serves the spring element as a support surface while a surface of the valve plate serves as an abutment.
  • the valve body is thus to manufacture from a single workpiece.
  • the attachment of the shoulder-like support surface and the groove are possible with the aid of a single tool by turning and / or milling.
  • Valve body, spring element and surface of the valve plate can be adapted to the circumference exactly to each other. Additional closure elements for the spring element are not required. It is equally possible to punch the spring element from a single spring steel plate.
  • the simple assembly of the spring element is used in this arranged extended insertion opening, which opens into the bore of the spring element.
  • the insertion opening may also be an enlarged bore, by means of which the spring element is pushed onto the head of the valve body, in order then to be laterally offset in the groove of the valve body.
  • the spring tension can be adapted to the high pressure of the flow medium.
  • the component can also be used because of its small design in a limited space environment, since no rotatable spring elements to be closed are provided.
  • the insertion opening can be arranged in the middle of the spring element or at the two outer ends.
  • a further embodiment of the invention has laterally, advantageously on both sides of the engaging in the groove of the valve body bore of the spring element a locking surface to give the spring element a reliable fit in the groove and exclude lateral displacement of the plate spring out of the groove.
  • the individual components of the conical valve need not be taken apart to install the spring element and can tense.
  • the insertion opening can be adapted to different valve body diameter.
  • a modified embodiment for the support surface of the valve body is that the support surface is arranged on a ring attached to the head of the valve body.
  • the ring can be mounted non-positively on the valve body after previously the spring element has been pushed onto the head by the head is passed through the bore of the spring element.
  • the flow opening for the fuel is closed by the valve body now against the valve plate force and form-fitting sealing, so that no additional sealing elements are required and a direct and direct opening or closing of the passage by means of the valve body is possible. Indirect sealing via a hydraulic system is not required.
  • a groove or channel is expediently arranged as a flow opening for the fuel.
  • the bearing surface of the spring element which rests on the valve housing not flat, but curved or wavy designed.
  • the wavy or curved shape serves as a compensation and ensures a secure fit, if the spring element is not rotationally symmetrical.
  • Fig. 1 shows a plan view of a valve plate 3, which has a recess 8.
  • a recessed, second recess 26 is inserted, in which a spring element 12 is inserted.
  • the spring element has an elongated rounded shape and is made of a thin sheet metal.
  • the second recess 26 has a shape that substantially corresponds to the width of the spring element 12, but longer than the spring element 12 is formed.
  • the spring element 12 is shown in Fig. 1 in the assembled state.
  • a valve body 5 is arranged, which is positively connected to the spring element 12.
  • a valve head 6 protrudes through a central bore 14 of the spring element 12.
  • the valve head 6 has a circular cross section whose diameter in the end region is greater than the diameter of the central bore 14.
  • the central bore 14 merges into two outer bores 13.
  • the outer bores 13 have a part-circular shape whose diameter is greater than the diameter of the valve head 6.
  • a surface 9 of the valve plate 3 is formed as a flat surface.
  • the recess 8 has a substantially circular cross-section.
  • Fig. 2 shows the valve plate 3 in cross-section AA of the figure.
  • the valve plate 3 has a valve bore 4, which opens into the second recess 26. In the direction of the second recess 26, the valve bore 4 tapers via a tapered valve seat 7.
  • a valve body 5 is introduced, which is conically formed via a sealing surface 27 to a groove 10 tapered.
  • the groove 10 defines a cylindrical portion of the valve body 5, which merges via the groove 10 in the valve head 6.
  • the valve head 6 has a larger diameter than the valve body 5 in the region of the groove 10.
  • the spring element 12 bears against the groove 10 with circular-segment-shaped edge regions of the central bore 14.
  • the spring element 12 is positively connected by the circular segment-shaped edge regions in the direction perpendicular to the longitudinal direction of the valve body 5 with the valve body 5. In addition, a displacement of the spring element 12 in the longitudinal direction of the valve body 5 due to the wider valve head 6 is not possible.
  • the spring element 12 has a cross-sectionally curved in the center region form, which rest with two end portions which are arranged in the region of the outer bores 13 on the valve plate 3 in the second recess 26.
  • a central region of the spring element 12, in which the central bore 14 is arranged, is lifted from a base surface of the second recess 26 and abuts against the valve head 6.
  • the valve body 5 is pressed by the deflection of the spring element 12 with the sealing surface 27 to the valve seat 7 of the valve plate 3.
  • the valve bore 4 in a flow direction 2, which leads from bottom to top, sealed.
  • the valve body 5 has a smaller cross-section in the valve bore 4 than the valve bore 4, so that fuel can flow from below to the valve seat 7.
  • valve body 5 is pressed against the biasing force of the spring element 12 from top to bottom, so that the sealing surface 27 of the valve body 5 lifts from the valve seat 7. This will be an opening in the Valve bore 4 is released, so that fuel can flow from below through the valve plate 3 upwards.
  • FIG. 3 shows a cross-section B-B through FIG. 1. It can clearly be seen that the spring element 12 rests directly against the valve head 6 in the region of the central bore 14. In the region of the groove 10, the valve body 5 has a smaller diameter than in the region of the valve head 6.
  • the central bore 14 has opposite, identical circular segments 28 as edge regions whose diameter substantially corresponds to the diameter of the valve body 5 in the region of the groove 10.
  • the central bore 14 is connected via intermediate regions 29 with the outer two holes 13.
  • the diameter of the outer bores 13 is greater than the diameter of the central bore 14 and at the same time greater than the diameter of the valve head 6.
  • the valve head 6 can be pushed through an outer bore 13 during assembly of the spring element 12 and then by a lateral displacement of the Spring element 12 relative to the valve body 5 a positive connection of the spring element 12 can be achieved with the valve body 5.
  • the intermediate region 29 of the spring element 12 is temporarily widened by the valve body 5 in the region of the groove 10 until the valve body 5 reaches the central bore 14.
  • the spring element 12 is made of an elastic material, preferably made of spring steel, so that the spring element 12 in the region of the intermediate regions 29 after pushing through the valve body 5 again assumes the original shape.
  • FIG. 5 shows the spring element 12 in a side view, in which the curved shape of the spring element 12 with a central curvature 31 is clearly recognizable.
  • the central curvature 31 is formed substantially in the region of the central bore 14
  • Fig. 6 shows the position of the spring element 12 during assembly and attachment to the valve body 5.
  • the spring element 12 is thereby arranged rightmost in the second recess 26.
  • the valve body 5 is inserted from below with the valve head 6 through the valve bore 4 and the valve head 6 pushed through the left outer bore 13.
  • the spring element 12 is displaced in a first mounting direction 17.
  • the mean curvature 31 of the spring element 12 is pressed in the direction of the valve plate 3. Since the spring element 12 rests with the right and left partial ring 30 on the valve plate 3, the valve body 5 is pulled into the valve seat 7 by this bias.
  • FIG. 10 shows an enlarged view of the second valve according to FIG. 9.
  • FIG. 8 shows a further embodiment of a valve in a plan view from the side of the recess 8.
  • the recess 8 instead of the second recess 26, a third recess 20 which is formed substantially cylindrical with two part-circular extension portions 32 is.
  • the third recess 20 is arranged under a further spring element 19.
  • the further spring element 19 is designed in the form of a circular disk with a central bore.
  • Fig. 9 shows the second valve of Figure 8 in section AA.
  • the further spring element 19 is fastened via a clamping ring 21 on the valve head 6 of the valve body 5.
  • the clamping ring 21 replaces the groove 10 and the widened version of the valve head according to the preceding figures.
  • the further spring element 19 essentially has a circular disk shape with a central bore. Through the central bore of the valve head 6 is guided.
  • the further spring element 19 also has a curved shape, wherein the further spring element 19 has an arcuate cross-section.
  • the further spring element 19 is fitted onto the valve head 6 until the further spring element 19 rests in the edge region on the valve plate 3. Subsequently, the further spring element 19 is pressed via a clamping ring 21 in the direction of the valve plate 3. Subsequently, the clamping ring 21 is pinched with the valve head 6, so that the further spring element 19 is positively connected to the valve body 5.
  • the further spring element 19 is biased against the valve plate 3, so that the valve body 5 is pulled against the valve seat 7 of the valve plate 3 by the bias of the further spring element 19.
  • Fig. 11 shows a third spring element 33 which is formed in the base in the form of a circular disc, but which has a central, circular curvature 34.
  • the cross section of the curvature 34 along a cross-sectional line 37 is formed symmetrically to a center axis M and substantially corresponds to the cross section of the spring element 12, as shown in Fig. 5.
  • the third spring element 33 is curved upwards in the edge region.
  • the third spring element 33 has a central bore 14, which are connected to outer bores 13 via intermediate regions 29 in accordance with the spring element 12.
  • the third spring element 33 shows a combination of the circular disk shape with the central bore 14 and the outer bores 13.
  • FIG. 12 shows, in a schematic representation, a fourth spring element 35, which has an essentially elongated shape.
  • the fourth spring element 35 is formed with a central bulge, wherein the end portions are bent upwards.
  • the fourth spring element 35 has a central, circular opening 36, which merges into lateral slots 38.
  • the lateral slots 38 are formed in the longitudinal direction of the fourth spring element 35.
  • the fourth spring element 35 is pushed for mounting with the bore 36 via a valve head 6 of an inserted into the valve plate 3 valve body 5.
  • the diameter of the bore 36 is slightly smaller than the diameter of the valve head 6, which merges via a step in a circumferential groove 10 as shown in FIG.
  • Fig. 13 shows schematically an injection valve with a 2/2-way valve, which is used as a servo valve and is formed according to the forms described in Figures 1 to 12.
  • high-pressure fuel from a high-pressure accumulator which is not shown, is supplied via a high-pressure bore 41 and an inlet bore 42 with an inlet throttle 43 to a control chamber 44 in an injection valve body 45.
  • the fuel pressure then acts on a rear end of an axially movable nozzle needle 46.
  • a movement of the nozzle needle 46 opens and closes injection holes 47 formed in the injection valve body 45 and leading to a combustion chamber of an internal combustion engine.
  • the injection holes 47 are connected to an injection chamber with a nozzle chamber 48 in connection.
  • the nozzle chamber 48 is formed at the front end of the nozzle needle 46 in the injection valve body 45 and connected to the high-pressure bore 41. If the full fuel pressure at the nozzle needle 46 is present both in the control chamber 44 and in the nozzle chamber 48, the nozzle needle 46 is pressed downwards due to the larger effective area in the control chamber 44, thereby closing the injection holes 47 a connection bore 51 in the injection valve body 45 with a discharge throttle 60 leads to a servo valve 49 integrated in the injection valve body 45, which in turn is connected to a fuel tank via a non-pressurized fuel return 59.
  • the servo valve is actuated and actuated via a valve tappet 56 by an electromagnetic or piezoelectric actuator 68.
  • the servo valve 49 has the task of controlling the pressure exerted on the movable nozzle needle 46 in the control chamber 44 for closing and opening the injection valve. If the servo valve 49 is closed, essentially the full fuel pressure is present in the control chamber 44, so that the nozzle needle 46 closes the injection holes 47, which lead into the combustion chamber of the internal combustion engine. If the actuator 58 is electrically actuated, then the valve stem 56 exerts a force on the servo valve 49 pressurized with a spring element 12, 19, 33, 35. As a result, the servo valve 49 opens, so that a connection between the high pressure accumulator, the control chamber 44, the servo valve 49 and the fuel return 64 sets.
  • the resulting fuel flow through the servo valve 49 leads to the inlet throttle 43 and the outlet throttle 60 to a defined pressure drop in the control chamber 44.
  • the fuel pressure acting in the control chamber 44 on the nozzle needle 46 decreases while the pressure in the nozzle chamber 48 remains the same so that the nozzle needle 46 lifts and injects fuel from the nozzle chamber 48 via the injection holes 47 into the combustion chamber of the internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Soupape pour un injecteur de carburant comprenant un boîtier de soupape qui présente un écoulement muni d'un siège de fermeture étanche, un corps de soupape, un élément élastique qui précontraint le corps de soupape sur le siège de fermeture étanche dans une position de fermeture, l'élément élastique (12, 19 ; 33, 34) étant disposé en aval du siège de fermeture étanche (7), caractérisée en ce que le corps de soupape (5) présente une gorge (10) et en ce que l'élément élastique (12, 33, 34) est maintenu dans la gorge (10) du corps de soupape (5) par un perçage central (14), le perçage central (14) débouchant dans un perçage (13) qui présente un plus grand diamètre que le perçage central (14), et un endroit rétréci qui possède un plus petit diamètre que le perçage central (14) étant prévu entre le perçage (13) et le perçage central (14).
  2. Soupape selon la revendication 1, caractérisée en ce que l'élément élastique (12, 19, 33 ; 34) est tendu entre le boîtier de soupape (1) et le corps de soupape (6).
  3. Soupape selon la revendication 1 ou 2, caractérisé en ce que le corps de soupape (5) présente une surface d'appui en forme d'épaulement, avec laquelle l'élément élastique (12, 19) est en contact.
  4. Soupape selon la revendication 1, 2 ou 3, caractérisée en ce que le perçage (13) présente un plus grand diamètre qu'une tête (6) du corps de soupape (5).
  5. Soupape selon la revendication 3, caractérisée en ce qu'il est prévu comme surface d'appui une bague de serrage (21) qui est fixée sur la tête (6) du corps de soupape (5).
  6. Soupape selon une des revendications 1 à 5, caractérisée en ce que l'élément élastique (12, 19 ; 33, 34) présente une courbure disposée au centre qui est dirigée dans le sens qui s'éloigne du boîtier de soupape (1).
  7. Soupape selon la revendication 6, caractérisée en ce que la courbure (31,
    34) est disposée dans la région dans laquelle l'élément élastique (12, 19 ; 33, 34) est fixée au corps de soupape (5).
  8. Soupape selon une des revendications 1 à 7, caractérisée en ce que le boîtier de soupape (1) présente un évidement muni d'une surface plane qui recevoit l'élément élastique (12, 19).
  9. Soupape selon une des revendications 1 à 8, caractérisée en ce que l'élément élastique (12, 19 ; 33, 34) présente des régions d'appui (30) et en ce que les régions d'appui (30) présentent une forme incurvée.
  10. Soupape selon une des revendications 1 à 9, caractérisée en ce que l'élément élastique (12, 19, 33, 34) est disposé sur le côté basse pression.
EP04737280A 2003-03-04 2004-02-25 Soupape comportant un element ressort pour un injecteur de carburant Expired - Lifetime EP1601869B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10309310 2003-03-04
DE10309310 2003-03-04
PCT/EP2004/001880 WO2004079180A1 (fr) 2003-03-04 2004-02-25 Soupape comportant un element ressort, conçue pour un injecteur de carburant

Publications (2)

Publication Number Publication Date
EP1601869A1 EP1601869A1 (fr) 2005-12-07
EP1601869B1 true EP1601869B1 (fr) 2007-11-14

Family

ID=32945825

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04737280A Expired - Lifetime EP1601869B1 (fr) 2003-03-04 2004-02-25 Soupape comportant un element ressort pour un injecteur de carburant

Country Status (3)

Country Link
EP (1) EP1601869B1 (fr)
DE (1) DE502004005498D1 (fr)
WO (1) WO2004079180A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7033835B1 (en) 1988-02-26 2006-04-25 Large Scale Biology Corporation Production of peptides in plants as viral coat protein fusions
DE102005024871A1 (de) * 2005-05-31 2006-12-07 Siemens Ag Injektor, insbesondere Kraftstoffinjektor
DE102005026979B4 (de) * 2005-06-10 2009-11-12 Siemens Ag Kraftstoffinjektor mit einer steuerbaren Ablaufdrossel einer Servoventil-Einheit zur Steuerung einer Düsennadel
DE102005032086B4 (de) * 2005-07-08 2014-03-27 Continental Automotive Gmbh Schaltventilvorrichtung und Einspritzventil
GB201314826D0 (en) * 2013-08-20 2013-10-02 Delphi Tech Holding Sarl Control Valve Arrangement
EP3317509B1 (fr) * 2015-07-02 2019-08-28 Robert Bosch GmbH Injecteur de carburant

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3855969T2 (de) * 1987-12-02 1998-03-05 Ganser Hydromag Elektromagnetisch betätigbare Vorrichtung zum schnellen Umschalten eines elektro-hydraulisch betätigten Kraftstoffeinspritzventils
DE19816316A1 (de) * 1998-04-11 1999-10-14 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19820341C2 (de) * 1998-05-07 2000-04-06 Daimler Chrysler Ag Betätigungsvorrichtung für eine Hochdruck-Einspritzdüse für flüssige Einspritzmedien

Also Published As

Publication number Publication date
DE502004005498D1 (de) 2007-12-27
EP1601869A1 (fr) 2005-12-07
WO2004079180A1 (fr) 2004-09-16

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